Scroll compressor

ABSTRACT

The present disclosure relates to a scroll compressor. According to the present disclosure, in a shaft penetration scroll compressor in which an eccentric portion of the rotation shaft is overlapped with a orbiting wrap of the orbiting scroll in a radial direction, when a bearing area between the orbiting scroll and the rotation shaft is A and an end plate area of the orbiting scroll is B, A/B may be formed in a range of 0.035-0.085, and thus it may be possible to obtain a sufficient volume ratio and Sommerfeld number as well as reducing the overall size of the compressor, thereby reducing a frictional loss and abrasion in the compressor.

CROSS-REFERENCE TO RELATED APPLICATIONS

The present disclosure relates to subject matter contained in priorityKorean Application No. 10-2011-0095471, filed on Sep. 21, 2011, which isherein expressly incorporated by reference in its entirety.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present disclosure relates to a scroll compressor.

2. Description of the Related Art

Scroll compressor may include a fixed scroll having a fixed wrap and aorbiting scroll having a orbiting wrap. The scroll compressor provides amethod of inhaling and compressing refrigerant through a continuousvolume change of the compression chamber formed between the fixed wrapand the orbiting wrap while the orbiting scroll performs a orbitingmovement on the fixed scroll.

Furthermore, the scroll compressor continuously performs inhalation,compression and discharge, and thus has excellent characteristics in theaspect of vibration and noise generated during its operational processcompared to other types of compressors.

In a scroll compressor, the behavior characteristic is determined by itstype of the fixed wrap and orbiting wrap. The fixed wrap and orbitingwrap may have an arbitrary shape, but typically have an involute curvedshape that can be easily processed. The involute curve denotes a curvecorresponding to a trajectory drawn by a cross section of thread whenunloosing thread wound around a base circle having an arbitrary radius.When using such an involute curve, the capacity change rate is constantbecause a thickness of the wrap is constant and thus the number of turnsshould be increased to obtain a sufficient level of compression ratio,but it may also increase the size of the compressor.

On the other hand, the orbiting scroll is typically formed with a diskshaped end plate and the orbiting wrap at the side of the end plate.Furthermore, a boss to portion is formed at a rear surface on which theorbiting wrap is not formed and connected to a rotation shaft fororbiting the orbiting scroll. Such a shape may form a orbiting wrap overa substantially overall area of the end plate, thereby decreasing adiameter of the end plate portion for obtaining the same compressionratio. However, on the contrary, the operating point to which arepulsive force of refrigerant is applied and the operating point towhich a reaction force for cancelling out the repulsive force is appliedare separated from each other in an axial direction, thereby causing aproblem of increasing vibration or noise while the orbiting scroll istilted during the operational process.

As a method for solving such problems, there has been disclosed aso-called shaft penetration scroll compressor which is a type that aposition at which the rotation shaft and the orbiting scroll arecombined with each other is formed on the same surface as the orbitingwrap. In such a type of compressor, the operating point of a repulsiveforce and the operating point of the reaction force are applied at thesame position, thereby solving a problem that the orbiting scroll isinclined. However, when the rotation shaft is extended to a orbitingwrap portion in such a manner, an end portion of the rotation shaft islocated at a central portion of the orbiting wrap, and accordingly, anintentional compression ratio can be obtained only when increasing thediameter of the end plate. As a result, it may increase the size of thecompressor.

Typically, in order to apply the compressor to an air conditioner, avolume ratio (Vr) of suction volume to discharge volume should besecured to be equal to or greater than 2.0, and a Sommerfeld number (Sf)capable of predicting the reliability of a bearing should be secured tobe equal to or greater than 0.005. However, a bearing between therotation shaft and the orbiting scroll penetrates a compression portionin a typical shaft penetration scroll compressor and thus it may bedifficult to secure the volume ratio (Vr) equal to or greater than 2.0without increasing the size of the compressor. Even so, when the size ofthe bearing is decreased to secure the volume ratio (Vr), the Sommerfeldnumber is also reduced, thereby causing a problem that the reliabilityof the bearing is decreased while generating a solid friction.

SUMMARY OF THE INVENTION

An object of the present disclosure is to provide a scroll compressorcapable of obtaining a sufficient volume ratio and Sommerfeld number aswell as reducing the overall size of the compressor.

In order to accomplish the objective of the present disclosure, there isprovided a scroll compressor including a fixed scroll having a fixedwrap; a orbiting scroll configured to have a orbiting wrap engaged withthe fixed wrap to form a first and a second compression chamber at aninner surface and an outer surface thereof, and perform a orbitingmovement against the fixed scroll; a rotation shaft configured to havean eccentric portion at an end portion thereof, and combined with theorbiting scroll such that the eccentric portion is overlapped with theorbiting wrap in a radial direction; and a driving unit configured todrive the rotation shaft, wherein when a bearing area between theorbiting scroll and the rotation shaft is A and an end plate area of theorbiting scroll is B, NB is formed in a range of 0.035-0.085.

Furthermore, there is provided a scroll compressor including a fixedscroll having a fixed wrap; a orbiting scroll configured to have aorbiting wrap engaged with the fixed wrap to form compression chambersat an inner surface and an outer surface thereof, respectively, andperform a orbiting movement against the fixed scroll; a rotation shaftconfigured to have an eccentric portion at an end portion thereof, andcombined with the orbiting scroll such that the eccentric portion isoverlapped with the orbiting wrap in a radial direction; and a drivingunit configured to drive the rotation shaft, wherein a rotation shaftcombining portion is formed at the orbiting scroll to be combined withthe rotation shaft, and an eccentric bearing combined with the rotationshaft combining portion to form the eccentric portion is combined withthe rotation shaft, and a value of a bearing area between an innercircumferential surface of the rotation shaft combining portion and anouter circumferential surface of the eccentric bearing divided by an endplate area of the orbiting scroll is formed in a range of 0.035-0.085.

BRIEF DESCRIPTION OF THE DRAWINGS

The accompanying drawings, which are included to provide a furtherunderstanding of the invention and are incorporated in and constitute apart of this specification, illustrate embodiments of the invention andtogether with the description serve to explain the principles of theinvention.

In the drawings:

FIG. 1 is a cross-sectional view schematically illustrating the internalstructure of a scroll compressor according to an embodiment of thepresent disclosure;

FIG. 2 is a partial cross-sectional view illustrating a compression unitin the embodiment illustrated in FIG. 1;

FIG. 3 is an exploded perspective view illustrating a compression unitillustrated in FIG. 2;

FIG. 4 is a plan view illustrating a first and a second compressionchamber immediately subsequent to inhalation and immediately prior todischarge in a scroll compressor having a orbiting wrap and a fixed wrapwith an involute shape;

FIG. 5 is a plan view illustrating a type of orbiting wrap in a scrollcompressor having a orbiting wrap and a fixed wrap with another involuteshape;

FIG. 6 is a plan view illustrating a orbiting wrap and a fixed wrapobtained by another envelope line;

FIG. 7 is an enlarged plan view illustrating a central portion thereofin FIG. 6;

FIG. 8 is a plan view illustrating a configuration in which the orbitingwrap is located prior to 150° starting discharge in the embodimentillustrated in FIG. 6;

FIG. 9 is a plan view illustrating a time point at which discharge isstarted from the second compression chamber in the embodimentillustrated in FIG. 6;

FIG. 10 is a schematic view illustrating a bearing area and an end platearea shown in a distinguished manner in the present embodiment; and

FIG. 11 is a graph illustrating a relation between a ratio of a bearingarea divided by an end plate area, a volume ratio and a Sommerfeldnumber in the embodiment illustrated in FIG. 10.

DETAILED DESCRIPTION OF THE INVENTION

Hereinafter, a scroll compressor according to the present disclosurewill be described in detail based on an embodiment illustrated in theaccompanying drawings.

Referring to FIG. 1, a scroll compressor according to the presentembodiment has a cylindrically shaped casing 110, and an upper shell 112and a lower shell 114 for covering an upper portion and a lower portionof the casing, respectively. The upper shell and lower shell are bondedto the casing to form one confined space together with the casing.

A discharge pipe 116 is provided at an upper portion of the upper shell112. The discharge pipe 116 corresponds to a path through whichcompressed refrigerant is discharged to the outside, and an oilseparator (not shown) for separating oil mixed with the dischargedrefrigerant may be connected to the discharge pipe 116. Furthermore, asuction pipe 118 is provided at a lateral surface of the casing 110. Asa path through which refrigerant to be compressed flows, the suctionpipe 118 is located at a boundary surface between the casing 110 and theupper shell 112 in FIG. 1, but the location may be set at discretion.Moreover, the lower shell 114 may also function as an oil chamber forstoring oil supplied to operate the compressor in an efficient manner.

A motor 120 as a driving unit is provided at a substantially centralportion of the inner portion of the casing 110. The motor 120 mayinclude a stator 122 fixed to an inner surface of the casing 110 and arotor 124 located at an inner portion of the stator 122 to be rotated byan interaction with the stator 122. A rotation shaft 126 is combinedwith the center of the rotor 124 and rotated together with the rotor124.

An oil passage 126 a is formed at an central portion of the rotationshaft 126 to be extended along a length direction of the rotation shaft126, and an oil pump 126 b for supplying oil stored in the lower shell114 to the upper portion thereof is provided at a lower end portion ofthe rotation shaft 126. The oil pump 126 b may have a shape in which aspiral groove is formed or a separate impeller is provided at an innerportion of the oil passage, and a separate capacity type pump may beprovided therein.

An enlarged diameter portion 126 c inserted into an inner portion of theboss portion formed on the fixed scroll which will be described later isformed at an upper end portion of the rotation shaft 126. The enlargeddiameter portion is formed to have a diameter larger than the otherportion thereof, and a pin portion 126 d forming an eccentric portiontogether with the eccentric bearing 128 which will be described later isformed at an end portion of the enlarged diameter portion. The eccentricbearing 128 is inserted into the pin portion 126 d to form an eccentricportion, and referring to FIG. 3, the eccentric bearing 128 iseccentrically inserted with respect to the pin portion 126 d, and acombining portion for both is asymmetrically formed in a substantially“D” shape based on the center of the pin portion such that the eccentricbearing 128 is not rotated with respect to the pin portion 126 d.

A fixed scroll 130 is mounted on a boundary portion between the casing110 and upper shell 112. The fixed scroll 130 is pushed and fixedbetween the casing 110 and the upper shell 112 in a shrink fit manner orcombined together with the casing 110 and upper shell 112 by welding.

A boss portion 132 into which the foregoing rotation shaft 126 isinserted is formed at a bottom surface of the fixed scroll 130. Apenetration hole through which the pin portion 126 d of the rotationshaft 126 passes is formed at an upper side surface (based on FIG. 1) ofthe boss portion 132 and thus the pin portion 126 d is protruded in theupward direction of the end plate portion 134 of the fixed scroll 130therethrough.

A fixed wrap 136 engaged with the orbiting wrap which will be describedlater to form a compression chamber is formed at an upper portionsurface of the end plate portion 134, and a space portion foraccommodating the orbiting scroll 140 which will be described later isformed, and a lateral wall portion 138 adjoining an innercircumferential surface of the casing 110 is formed at an outercircumferential portion of the end plate portion 134. A orbiting scrollsupport portion 138 a on which an outer circumferential portion of theorbiting scroll 140 is placed is formed at an inner side of the upperend portion of the lateral wall portion 138, and the height of theorbiting scroll support portion 138 a is formed to have the same heightas the fixed wrap 136 or to have a height slightly less than that of thefixed wrap, and thus an end portion of the orbiting wrap can be broughtinto contact with a surface of the end plate portion of the fixedscroll.

The orbiting scroll 140 is provided at an upper portion of the fixedscroll 130. The orbiting scroll 140 is formed with a substantiallyorbiting shaped end plate portion 142 and a orbiting wrap 144 engagedwith the fixed wrap 136. A substantially orbiting shaped rotation shaftcombining portion 146 rotatably inserted and fixed to the eccentricbearing 128 is formed at a central portion of the end plate portion 142.An outer circumferential portion of the rotation shaft combining portion146 is connected to the orbiting wrap to perform the role of forming acompression chamber together with the fixed wrap during the compressionprocess. It will be described later.

On the other hand, the eccentric bearing 128 is inserted into therotation shaft combining portion 146 and thus an end portion of therotation shaft 126 is inserted through the end plate portion of thefixed scroll, and the orbiting wrap, fixed wrap and eccentric bearing128 are provided to be overlapped with one another in the radialdirection of the compressor. During compression, a repulsive force ofrefrigerant is applied to the fixed wrap and orbiting wrap, and acompression force is applied between the rotation shaft support portionand eccentric bearing as a reaction force thereto. As described above,when part of the shaft is overlapped with the wrap in a radial directionthrough the end plate portion, the repulsive force and compression forceof refrigerant are applied to the same surface based on the end plate,and thus they are cancelled out by each other. Due to this, it may bepossible to prevent the inclination of the orbiting scroll by theoperation of the compression force and repulsive force.

Furthermore, though not shown in the drawing, a discharge hole is formedon the end plate portion 142 and thus compressed refrigerant may bedischarged to an inner portion of the casing. The location of thedischarge hole may be set at discretion by taking a required dischargepressure or the like into consideration.

Furthermore, an oldham ring 150 for preventing the rotation of theorbiting scroll is provided at an upper side of the orbiting scroll 140.The oldham ring 150 may include a substantially orbiting shaped ringportion 152 inserted into a rear surface of the orbiting scroll 140 anda pair of first key 154 and second key 156 which are protruded on alateral surface of the ring portion 152. The first key 154 is protrudedfarther than the thickness of an outer circumferential side of the endplate portion 142 of the orbiting scroll 140, and inserted into an innerportion of the first key groove 154 a formed over an upper end of thelateral wall portion 138 of the fixed scroll 130 and the orbiting scrollsupport portion 138 a. Moreover, the second keys 156 are combined withthe second key grooves 156 a, respectively, formed at an outercircumferential portion of the end plate portion 142 of the orbitingscroll 140 in the state of being inserted therein.

Here, the first key groove 154 a is formed to have a vertical portionextended in the upward direction and a horizontal portion extended inthe left/right direction, and a lower side end portion of the first key154 always maintains a state of being inserted in the horizontal portionof the first key groove 154 a, but an outer side end portion of thefirst key 154 in the radial direction is formed to be released from thevertical portion of the first key groove 154 a during the orbitingmovement of the orbiting scroll. In other words, a coupling between thefirst key groove 154 a and the fixed scroll is made in the verticaldirection, thereby reducing the diameter of the fixed scroll.

Specifically, a clearance as much as corresponding to a orbiting radiusshould be secured between an end plate of the orbiting scroll and aninner wall of the fixed scroll. If a key of the oldham ring is combinedwith the fixed scroll in the radial direction, then the length of a keygroove formed on the fixed scroll should be at least greater than theorbiting radius to prevent the oldham ring from being released from thekey groove during the orbiting process, and it may be a cause ofincreasing the size of the fixed scroll.

On the contrary, as in the above embodiment, if the key groove isextended to a lower space between the end plate and the orbiting wrap inthe orbiting scroll, it may be possible to secure a sufficient length ofthe key groove and reducing the size of the fixed scroll.

Moreover, in the above embodiment, all keys are formed at a lateralsurface of the ring portion, and thus the height of the compression unitin the axial direction can be reduced compared to a case that keys areformed, respectively, in both lateral surfaces thereof.

On the other hand, a lower frame 160 for rotatably supporting a lowerside of the rotation shaft 126 is provided at a lower portion of thecasing 110, and the orbiting scroll and an upper frame 170 forsupporting the oldham ring 150 are provided, respectively, at an upperportion of the orbiting scroll. A hole communicated with a dischargehole of the orbiting scroll 140 to discharge compressed refrigerant tothe side of the upper shell is formed at the center of the upper frame170.

FIG. 4 is a plan view illustrating a compression chamber immediatelysubsequent to inhalation and a compression chamber immediately prior todischarge in a scroll compressor having a orbiting wrap and a fixed wrapformed with an involute curve, and having a configuration that part ofthe shaft penetrates the end plate. FIG. 4A is a view illustrating achange of the first compression chamber formed between an inner lateralsurface of the fixed wrap and an outer lateral surface of the orbitingwrap, and FIG. 4B is a view illustrating a change of the secondcompression chamber formed between an inner lateral surface of theorbiting wrap and an outer lateral surface of the fixed wrap.

In the scroll compressor, the compression chamber is created between twocontact points generated when the fixed wrap and orbiting wrap arebrought into contact with each other, and in case of the fixed wrap andorbiting wrap with an involute curve, two contact points defining onecompression chamber as illustrated in FIG. 4 are located on a straightline. In other words, the compression chamber is disposed over 360° withrespect to the center of the rotation shaft.

Considering a volume change of the first compression chamber in FIG. 4A,the volume of the compression chamber immediately subsequent toinhalation located at the outside is gradually reduced while moving tothe central portion thereof by a orbiting movement of the orbitingscroll, and thus has a minimum value when reaching an outercircumferential portion of the rotation shaft combining portion locatedat the center of the orbiting scroll. In case of the fixed wrap andorbiting wrap with an involute curve, the volume reduction rate islinearly reduced as increasing the rotation angle of the rotation shaft,and thus the compression chamber should be moved closely to the centerif possible, to obtain a high compression ratio, but in case where therotation shaft exists at the center as described above, it can be movedonly to an outer circumferential portion of the rotation shaft. Due tothis, the compression ratio is reduced, and the compression ratio isabout 2.13 in FIG. 4A.

On the other hand, the second compression chamber illustrated in FIG. 4Bhas a lower compression ratio compared to the first compression chamber,and thus has a value of about 1.46. However, in case of the secondcompression chamber, when a connecting portion between the rotationshaft combining portion (P) and the orbiting wrap is formed with aorbiting arc shape as illustrated in FIG. 5A, a compression path of thesecond compression chamber is lengthened, thereby increasing thecompression ratio up to a level of 3.0. In this case, the secondcompression chamber has a range of less than 360 degrees immediatelyprior to discharge. However, such a method cannot be applicable to thefirst compression chamber.

Accordingly, in case of the fixed wrap and orbiting wrap with aninvolute shape, an intentional level of compression ratio can beobtained in case of the second compression chamber, but it is impossiblein case of the first compression chamber, and as a result, in case thatthere is a remarkable difference of compression ratio between the twocompression chambers, it will affect a bad effect on the operation ofthe compressor.

In order to solve the foregoing problem, the fixed wrap and orbitingwrap may be formed to have another curve other than the involute curve.Referring to FIGS. 6 and 7, when the center of the rotation shaftcombining portion 146 is “O”, and two contact points are “P1, P2”,respectively, it is seen that an angle a defined by two straight linesconnecting the two contact points (P1, P2) to the center (O) of therotation shaft combining portion is less than 360°, and also a distance“I” between perpendicular vectors at each contact point has a valuegreater than “0”. Due to this, the first compression chamber immediatelyprior to discharge has a volume less than a case of the fixed wrap andorbiting wrap formed with an involute curve, thereby increasing thecompression ratio. Furthermore, the orbiting wrap and fixed wrapillustrated in FIG. 6 have a configuration in which the diameter andstarting point thereof are connected to a plurality of differentorbiting arcs, and the outermost curve has a substantially oval shapehaving the major and minor axes.

Furthermore, a protrusion portion 137 protruded to the side of therotation shaft combining portion 146 is formed adjacent to an inner sideend portion of the fixed wrap, and a contact portion 137 a formed to beprotruded from the protrusion portion is additionally formed on theprotrusion portion 137. In other words, the inner side end portion ofthe fixed wrap is formed to have a thickness greater than the otherportion thereof. Due to this, a strength of the inner side end portionof the wrap receiving the highest compression force on the fixed wrapcan be enhanced, thereby enhancing the durability.

On the other hand, the thickness of the fixed wrap is graduallydecreased from the contact point (P1) located at an inner side betweenthe two contact points forming the first compression chamber at adischarge start time point as illustrated in FIG. 7. Specifically, afirst decreasing portion 137 b adjacent to the contact point (P1) and asecond decreasing portion 137 c adjacent to the first decreasing portionare formed, and a thickness reduction rate at the first decreasingportion is greater than that at the second decreasing portion.Furthermore, the thickness of the fixed wrap is increased for apredetermined section subsequent to the second decreasing portion.

Furthermore, when a distance between an inner surface of the fixed wrapand the axial center (O′) of the rotation shaft is DF, the DF isdecreased after being increased as moving in a counter clockwisedirection (based on FIG. 7) from the P1, and the section thereof isshown in FIG. 8. FIG. 8 is a plan view illustrating the location of theorbiting wrap prior to 150° starting discharge, and the orbiting wrapreaches a configuration illustrated in FIG. 6 when the rotation shaft isfurther rotated by 150° from the configuration of FIG. 8. Referring toFIG. 8, the contact point is located at an upper side of the rotationshaft combining portion 146, and the DF is increased and then decreasedduring the section between P1 of FIGS. 6 and P1 of FIG. 8.

A concave portion 145 engaged with the protrusion portion is formed atthe rotation shaft combining portion 146. A lateral surface of theconcave portion 145 is brought into contact with the contact portion 137a of the protrusion portion 137 to form a side contact point of thefirst compression chamber. When a distance between the center of therotation shaft combining portion 146 and an outer circumferentialportion of the rotation shaft combining portion 146 is “Do”, the “Do” isincreased and then decreased during the section between P1 of FIGS. 6and P1 of FIG. 8. Similarly, the thickness of the rotation shaftcombining portion 146 is also increased and then decreased during thesection between P1 of FIGS. 6 and P1 of FIG. 8.

Furthermore, a side wall of the concave portion 145 may include a firstincreasing portion 145 a in which the thickness thereof is drasticallyincreased in a relatively high rate and a second increasing portion 145b connected to the first increasing portion in which the thickness isincreased in a relatively low rate. They correspond to the firstdecreasing portion and the second decreasing portion, respectively. Thefirst increasing portion, first decreasing portion, second increasingportion, and second decreasing portion are obtained as a result ofbending the envelope line toward the rotation shaft combining portion.Due to them, an inner side contact point (P1) forming the firstcompression chamber is located at the first increasing portion andsecond increasing portion, and as a result, the compression ratio can beincreased by decreasing the length of the first compression chamberimmediately prior to discharge.

The other side wall of the concave portion 145 is formed to have aorbiting arc shape. The diameter of the orbiting arc is determined by awrap thickness of the end portion of the fixed wrap and a orbitingradius of the orbiting wrap, and the diameter of the orbiting arc isincreased as increasing the thickness of the end portion of the fixedwrap. Due to this, the thickness of the orbiting wrap around theorbiting arc is also increased to secure the durability, and thecompression path is lengthened and thus has an advantage of increasingthe compression ratio of the second compression chamber as much as thelengthened path.

Here, a central portion of the concave portion 145 forms part of thesecond compression chamber. FIG. 9 is a plan view illustrating thelocation of the orbiting wrap when discharge is started from the secondcompression chamber, and the second compression chamber is locatedadjacent to a orbiting shaped side wall of the concave portion in FIG.9, and when the rotation shaft is further rotated, an end portion of thesecond compression chamber passes through a central portion of theconcave portion.

On the other hand, as described above, in order to apply the compressorto an air conditioner, a ratio (Vr) of suction volume to dischargevolume should be secured to be equal to or greater than 2.0, and aSommerfeld number (Sf) should be secured to be equal to or greater than0.005, but it is not easy to satisfy the condition without increasingthe size of the compressor in a shaft penetration scroll compressor.However, as illustrated in FIG. 7, in case where A/B is formed to be ina range of 0.035-0.085 when a bearing area between the orbiting scrolland rotation shaft is A and an end plate area of the orbiting scroll(including the bearing area) is B, it may be expected to have a resultof satisfying the above condition.

FIG. 10 is a schematic view illustrating a bearing area and an end platearea shown in a distinguished manner in the present embodiment, and FIG.11 is a graph illustrating a relation between a value (hereinafter, arearatio) of a bearing area divided by an end plate area, a volume ratioand a Sommerfeld number. As illustrated in the drawing, the volume ratiohas a relation that the Sommerfeld number is in inverse proportion tothe area ratio. In other words, the Sommerfeld number is decreased asincreasing the volume ratio whereas the volume ratio is decreased asincreasing the Sommerfeld number at the same area ratio. Accordingly, inorder to secure a proper volume ratio and Sommerfeld number, it ispreferable to secure a proper area ratio (NB) as illustrated in FIG. 11.When the area ratio (NB) is designed to maintain 0.035-0.085 in thepresent embodiment, it may be possible to obtain a sufficient volumeratio and Sommerfeld number, thereby performing the compressorperformance required for an air conditioner without increasing the sizeof the compressor as well as reducing a frictional loss and abrasion inthe orbiting scroll and rotation shaft.

The area ratio according to the present embodiment may be uniformlyapplicable to all shaft penetration scroll compressors.

What is claimed is:
 1. A scroll compressor, comprising: a fixed scrollhaving a fixed wrap; a orbiting scroll configured to have a orbitingwrap engaged with the fixed wrap to form a first and a secondcompression chamber at an inner surface and an outer surface thereof,and perform a orbiting movement against the fixed scroll; a rotationshaft configured to have an eccentric portion at an end portion thereof,and combined with the orbiting scroll such that the eccentric portion isoverlapped with the orbiting wrap in a radial direction; and a drivingunit configured to drive the rotation shaft, wherein when a bearing areabetween the orbiting scroll and the rotation shaft is A and an end platearea of the orbiting scroll is B, A/B is formed in a range of0.035-0.085.
 2. The scroll compressor of claim 1, wherein the firstcompression chamber is formed between two contact points (P1, P2)generated when an inner surface of the fixed wrap and an outer surfaceof the orbiting wrap are brought into contact with each other, and whenan angle having a greater value between angles made by two linesconnecting the center (O) of the eccentric portion to the two contactpoints (P1, P2), respectively, is α, α<360° at least prior to startingdischarge.
 3. The scroll compressor of claim 2, wherein when a distancebetween perpendiculars at the two contact points (P1, P2) is I, I>0. 4.The scroll compressor of claim 1, wherein a rotation shaft combiningportion combined with the eccentric portion at an inner portion thereofis formed at a central portion of the orbiting scroll, and a protrusionportion is formed at an inner circumferential surface of an inner endportion of the fixed wrap, and a concave portion brought into contactwith the protrusion portion to form a compression chamber is formed atan outer circumferential surface of the rotation shaft combiningportion.
 5. The scroll compressor of claim 1, wherein the rotation shaftcomprises: a shaft portion connected to the driving unit; a pin portionconcentrically formed with the shaft portion at an end portion of theshaft portion; and an eccentric bearing eccentrically combined with thepin portion to form the eccentric portion, wherein the eccentric bearingis rotatably combined with the rotation shaft combining portion.
 6. Thescroll compressor of claim 5, wherein the pin portion is formed to havean asymmetric shape based on the center thereof.
 7. A scroll compressor,comprising: a fixed scroll having a fixed wrap; a orbiting scrollconfigured to have a orbiting wrap engaged with the fixed wrap to formcompression chambers at an inner surface and an outer surface thereof,respectively, and perform a orbiting movement against the fixed scroll;a rotation shaft configured to have an eccentric portion at an endportion thereof, and combined with the orbiting scroll such that theeccentric portion is overlapped with the orbiting wrap in a radialdirection; and a driving unit configured to drive the rotation shaft,wherein a rotation shaft combining portion is formed at the orbitingscroll to be combined with the rotation shaft, and an eccentric bearingcombined with the rotation shaft combining portion to form the eccentricportion is combined with the rotation shaft, and a value of a bearingarea between an inner circumferential surface of the rotation shaftcombining portion and an outer circumferential surface of the eccentricbearing divided by an end plate area of the orbiting scroll is formed ina range of 0.035-0.085.
 8. The scroll compressor of claim 7, wherein thefirst compression chamber is formed between two contact points (P1, P2)generated when an inner surface of the fixed wrap and an outer surfaceof the orbiting wrap are brought into contact with each other, and whenan angle having a greater value between angles made by two linesconnecting the center (O) of the eccentric portion to the two contactpoints (P1, P2), respectively, is α, α<360° at least prior to startingdischarge.
 9. The scroll compressor of claim 8, wherein when a distancebetween perpendiculars at the two contact points (P1, P2) is I, I>0. 10.The scroll compressor of claim 7, wherein a rotation shaft combiningportion combined with the eccentric portion at an inner portion thereofis formed at a central portion of the orbiting scroll, and a protrusionportion is formed at an inner circumferential surface of an inner endportion of the fixed wrap, and a concave portion brought into contactwith the protrusion portion to form a compression chamber is formed atan outer circumferential surface of the rotation shaft combiningportion.